CN103410803A - Pilot operated directional control valve, coordinated control hydraulic system and hydraulic control system of excavator - Google Patents
Pilot operated directional control valve, coordinated control hydraulic system and hydraulic control system of excavator Download PDFInfo
- Publication number
- CN103410803A CN103410803A CN2013103510815A CN201310351081A CN103410803A CN 103410803 A CN103410803 A CN 103410803A CN 2013103510815 A CN2013103510815 A CN 2013103510815A CN 201310351081 A CN201310351081 A CN 201310351081A CN 103410803 A CN103410803 A CN 103410803A
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- hydraulic
- control
- control valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a pilot operated directional control valve, a coordinated control hydraulic system and a hydraulic control system of an excavator. Plungers (8 and 9) and control ports (A1 and A4) are arranged in pilot operated valves (6 and 7) of the pilot operated directional control valve, so that openness of an opening of the valve can be effectively adjusted by guiding control oil in from the control ports. The pilot operated directional control valve serves as a rotation operation valve in the coordinated control hydraulic system and the hydraulic control system of the excavator, and a pilot control oil way for controlling lifting of a movable arm in a movable arm operation valve is connected with the control ports of the pilot operation directional control valve, so that during movable arm lifting and rotation linkage, the openness of the opening of the rotation operation valve is relatively reduced, throttling is generated, oil source pressure is improved to push a movable arm cylinder to extend out, and low-load rotation and high-load movable arm cylinder linkage can be achieved. In addition, the problem of coordination of movable arm downward placing and rotation and linkage can be solved by setting a feedback oil supply way (FK) and a feedback reversing valve (15).
Description
Technical field
The invention belongs to the hydraulic system technical field of engineering machinery, particularly, hydraulic system is controlled in the pilot operated directional control valve and the interlock that relate to a kind of hydraulic control system of excavator and wherein application.
Background technique
The interlock of a plurality of actuators is very common in the operation process of hydraulic shovel, and the interlock of revolution and swing arm is one of them.For example when ditching operation, swing arm completely struggles against and promotes revolution interlock simultaneously, and after discharging, the swing arm zero load is transferred and rotating interlock.Usually swing arm completely struggles against and promotes required pressure higher than the required pressure of revolution, therefore when the two links, there will be revolution action to be arranged and the situation of swing arm attonity.On the other hand, the pressure that the swing arm zero load is transferred, lower than the required pressure of revolution, therefore, there will be swing arm action to be arranged and the situation of revolution attonity when the two links.
In patent CN 101793042A, introduce a kind of oil hydraulic circuit be used to realizing that Hydraulic Excavator's Boom and revolution link, effectively solved the harmony that swing arm completely struggles against and promotes and turn round action.As shown in Figure 1, because completely struggling against, swing arm promotes required pressure higher than the required pressure of revolution, it is low that hydraulic oil in working connection P1 is preferably supplied with pressure, therefore by being set, throttle valve 9, shuttle valve 10 and the pressure release oil circuit by fluid-controlled cut-off valve 4 oil returns thereof reduce the pilot control pressure in the pilot control oil circuit in the slewing directional control valve 3 of rotary motor 2, thereby reduce the open amount of slewing directional control valve 3, from the fluid flow that enters rotary motor 2 working connection P1, be minimized, the boost in pressure of working connection also enters swing arm selector valve 1 and boom cylinder 5.Further, in the pilot control oil circuit of slewing directional control valve 3, be provided with throttle valve 6, the pressure balance that enters the pilot pressure oil of swing arm selector valve 1 and slewing directional control valve 3 from turning round manual pilot valve 7 and swing arm manual pilot valve 8 with making, reduce to enter the pilot pressure oil flow of slewing directional control valve 3, avoided the hydraulic oil in guide's working connection P2 preferably to supply with slewing directional control valve 3.Although this coordinated control system has solved the interlock control that swing arm completely struggles against and promotes and turn round action, but and fail to solve the swing arm zero load and transfer and the harmony problem of turning round the action interlock, namely load is lower when swing arm is transferred, load was higher when revolution was rotated, if the two moves the problem of likely turning round attonity simultaneously.
Summary of the invention
The hydraulic control system that the purpose of this invention is to provide a kind of pilot operated directional control valve, interlock control hydraulic system and excavator, the harmony problem linked effectively to solve swing arm and revolution.
For achieving the above object, according to an aspect of the present invention, a kind of pilot operated directional control valve is provided, comprise valve body and spool, described spool can axially movably be arranged in the valve pocket of described valve body, between the first end of this spool and the first end of described valve pocket, be formed with the first liquid controling cavity, and be formed with the second liquid controling cavity between the second end of this spool and the second end of described valve pocket, wherein, described pilot operated directional control valve also comprises the first plunger and the second plunger, this first plunger and the second plunger can axially movably be separately positioned in described the first liquid controling cavity and the second liquid controling cavity and form cylinder and be sealed and matched, described valve body is provided with first and controls mouth, second controls mouth, the 3rd controls mouth and the 4th controls mouth, described first controls mouth is set to pass in the chamber between the first end of described the first plunger and described valve pocket of described the first liquid controling cavity, described second controls mouth is set to pass in the chamber between the first end of described the first plunger and described spool of described the first liquid controling cavity, the described the 3rd controls mouth is set to pass in the chamber between the second end of described the second plunger and described spool of described the second liquid controling cavity, the described the 4th controls mouth is set to pass in the chamber between the second end of described the second plunger and described valve pocket of described the second liquid controling cavity.
Preferably, preferably, described the first control mouth and the 4th is controlled mouth and is interconnected.
Preferably, the two ends of described valve body are respectively equipped with plug section, form respectively described the first liquid controling cavity and the second liquid controling cavity between the two ends of described spool and corresponding described plug section.
Preferably, this pilot operated directional control valve also comprises the first spring that is positioned at described the first liquid controling cavity and the second spring that is positioned at described the second liquid controling cavity, described the first spring and the second spring all are set on the valve seat of an end pressure-bearing in described valve body, and the other end is biased on the respective end of described spool.
Preferably, this pilot operated directional control valve is three six-way transfer valves, described valve body is provided with filler opening, return opening, the first connecting port, the second connecting port, the first actuator port and the second actuator port be communicated in described valve pocket, when described spool mediates, described the first connecting port is communicated with described the second connecting port, and described the first actuator port and the second actuator port all end conducting with described filler opening and return opening.
According to another aspect of the present invention, provide a kind of interlock to control hydraulic system, comprise the first operation control system of system oil-feed oil circuit, system oil return oil circuit, the first control valve and control thereof and the second operation control system of the second control valve and control thereof, wherein, described the first control valve is the pilot operated directional control valve above-mentioned according to the present invention, in described the first control valve described second controlled mouth and is connected with the first pilot control oil circuit, and the described the 3rd controls mouth is connected with the second pilot control oil circuit;
Described the second control valve is pilot operated directional control valve, the both sides hydraulic control mouth of this pilot operated directional control valve is connected with respectively be used to the 3rd pilot control oil circuit and the 4th pilot control oil circuit of realizing that the guide is commutated, and described the 3rd pilot control oil circuit also is communicated with described first in described the first control valve and controls mouth and the 4th control mouthful;
And described system oil-feed oil circuit is connected respectively to the filler opening of described the first control valve and the filler opening of the second control valve, and the return opening of the return opening of described the first control valve and the second control valve all is connected to described system oil return oil circuit.
Preferably, described the first control valve and the second control valve are three six-way transfer valves and comprise respectively filler opening, return opening, connecting port and actuator port, wherein, the described system oil-feed of the first connecting port hydraulic connecting oil circuit of described the first control valve, the second connecting port is pressed and is connected with the third connecting oral fluid of the second control valve, and the 4th connecting port of described the second control valve is communicated with described system oil return oil circuit.
Preferably, described the second operation control system comprises operating cylinder, the rod chamber of this operating cylinder is connected to the first actuator port in the described actuator port of described the second control valve by the rod chamber working oil path, the rodless cavity of described operating cylinder is connected to the second actuator port in the described actuator port of described the second control valve by the rodless cavity working oil path;
Wherein, described interlock is controlled hydraulic system and is also comprised the feedback selector valve be arranged in described rodless cavity working oil path, in this feedback selector valve, be provided with the first hydraulic fluid port, the second hydraulic fluid port and the 3rd hydraulic fluid port and have the first commutation position and the second commutation position, the second actuator port of described the second control valve of described the first hydraulic fluid port hydraulic connecting, the rodless cavity of the described operating cylinder of described the second hydraulic fluid port hydraulic connecting, be connected with the feedback oil feeding line between the described filler opening of described the 3rd hydraulic fluid port and described the first control valve; At described the first commutation position, described the second hydraulic fluid port is communicated with the first hydraulic fluid port and is communicated with described the 3rd hydraulic fluid port cut-off, at described the second commutation position, described the second hydraulic fluid port is communicated with by the first internal oil passages with the first hydraulic fluid port, and described the second hydraulic fluid port is communicated with by the second internal oil passages with the 3rd hydraulic fluid port and described the second internal oil passages is provided with the first throttle valve.
Preferably, in described the second control valve, control bit corresponding to described the 4th pilot control oil circuit is arranged so that described the first actuator port is communicated with described filler opening, described the second actuator port connects oil circuit by inside and is communicated with described return opening, and described inner the connection in oil circuit is provided with the second throttle valve.
Preferably, described feedback selector valve is pilot operated directional control valve, in the hydraulic control guide oil circuit of this feedback selector valve, be provided with pilot reversing valve and shuttle valve, described shuttle valve has the first filler opening, the second filler opening and oil outlet, described pilot reversing valve has the first control port, first connects hydraulic fluid port, second connects hydraulic fluid port is connected hydraulic fluid port with the 3rd, described the 4th pilot control oil circuit of described control port hydraulic connecting, described first connects the second control port of the described feedback selector valve of hydraulic fluid port hydraulic connecting, described second connects the described system oil return oil circuit of hydraulic fluid port hydraulic connecting, the described the 3rd connects the oil outlet of the described shuttle valve of hydraulic fluid port hydraulic connecting, and the first filler opening of described shuttle valve connects described the first pilot control oil circuit, the second filler opening connects described the second pilot control oil circuit.
Preferably, described interlock is controlled hydraulic system and is also comprised one-way hydraulic lock, and this one-way hydraulic lock is arranged on the oil circuit part between the second hydraulic fluid port of the rodless cavity of the described operating cylinder in described rodless cavity working oil path and described feedback selector valve.
Preferably, be provided with the feedback one-way valve in described feedback oil feeding line, this feedback one-way valve is arranged so that hydraulic oil can flow to from the 3rd hydraulic fluid port of described feedback selector valve the first filler opening of described the first control valve and oppositely cut-off.
Preferably, described system oil-feed oil circuit by the first oil-feed oil circuit and the second oil-feed oil circuit respectively to the filler opening of described the first control valve and the filler opening fuel feeding of described the second control valve, described the second oil-feed oil circuit of one end hydraulic connecting of described the first oil-feed oil circuit, the other end hydraulic connecting is on the filler opening at described the first control valve and the oil circuit part between described feedback one-way valve of described feedback oil feeding line; Wherein said interlock is controlled hydraulic system and is also comprised the first in line check valve and the second in line check valve, described the first in line check valve is arranged in described the second oil-feed oil circuit, so that hydraulic oil can flow to the filler opening of described the second control valve and oppositely cut-off from described system oil-feed oil circuit, described the second in line check valve is arranged on described the first oil-feed oil circuit, so that hydraulic oil can flow to the filler opening of described the first control valve and oppositely cut-off by described the first oil-feed oil circuit from described system oil-feed oil circuit.
According to also aspect of the present invention, a kind of hydraulic control system of excavator is provided, the hydraulic control system of this excavator comprises the interlock control hydraulic system above-mentioned according to the present invention, wherein said the first operation control system is the revolution operation control system, described the second operation control system is the swing arm operation control system, described the 3rd pilot control oil circuit is carried out stretch for controlling described swing arm operation control system, and described the 4th pilot control oil circuit is carried out the action of contracting arm for controlling described swing arm operation control system.
According to technique scheme, by plunger being set and controlling mouth in liquid controling cavity, control fluid can promote plunger and spool moves effectively to regulate valve port opening in the situation that pass into from this control mouth in pilot operated directional control valve of the present invention.In the hydraulic control system that adopts this pilot operated directional control valve as the interlock control hydraulic system of turning round control valve and excavator, the control mouth of above-mentioned pilot operated directional control valve will be connected to for the pilot control oil circuit of controlling the swing arm lifting in the swing arm control valve, make when swing arm promotes and turn round interlock, valve port opening in the revolution control valve reduces relatively, produce throttling, make the pressure of pressure oil-source raise, and then promote the higher boom cylinder of load and stretch out, realize revolution action and the higher boom cylinder interlock of load that load is lower.Further, interlock of the present invention is controlled in hydraulic system between the filler opening by the rodless cavity working oil path at boom cylinder and revolution control valve and the hydraulic element such as feedback oil feeding line and pilot operated directional control valve are set have also been solved the swing arm zero load and transfer and turn round the harmony problem that action links.
Other features and advantages of the present invention will partly be described in detail in embodiment subsequently.
The accompanying drawing explanation
Accompanying drawing is to be used to provide a further understanding of the present invention, and forms the part of specification, with following embodiment one, is used from explanation the present invention, but is not construed as limiting the invention.In the accompanying drawings:
Fig. 1 is the swing arm of applying in a kind of excavator of prior art and turns round the hydraulic schematic diagram that hydraulic system is controlled in interlock;
Fig. 2 is the structural representation according to a kind of pilot operated directional control valve of the preferred embodiment of the present invention; With
Fig. 3 controls the hydraulic schematic diagram of hydraulic system according to the interlock of the preferred embodiment of the present invention.
Description of reference numerals of the present invention
1 valve body 2 spools
3 valve pocket 4 first plug sections
5 second plug section 6 first liquid controling cavities
7 second liquid controling cavity 8 first plungers
9 second plunger 10 valve seats
11 first spring 12 second springs
13 operating cylinder 14 one-way hydraulic locks
15 feedback selector valve 16 pilot reversing valves
17 shuttle valve 18 feedback one-way valves
19 first in line check valve 20 second in line check valves
100 first control valve 200 second control valves
300 first operation control system 400 second operation control systems
151 first throttle valve 201 second throttle valve
A1 first controls mouthful A2 second and controls mouth
A3 the 3rd controls mouthful A4 the 4th and controls mouth
B1 first connects hydraulic fluid port B2 second and connects hydraulic fluid port
B3 the 3rd connects hydraulic fluid port C1 the first hydraulic fluid port
C2 the second hydraulic fluid port C3 the 3rd hydraulic fluid port
P1 oil inlet P 2 filler openings
T1 oil return inlet T 2 return openings
L1 first connecting port L2 the second connecting port
L3 third connecting mouth L4 the 4th connecting port
M1 first actuator port M2 the second actuator port
N1 first actuator port N2 the second actuator port
K1 first control port K2 the second control port
Y rod chamber W rodless cavity
P system oil-feed oil circuit T system oil return oil circuit
XAs first pilot control oil circuit XBs the second pilot control oil circuit
XAb the 3rd pilot control oil circuit XBb the 4th pilot control oil circuit
Ab rodless cavity working oil path Bb rod chamber working oil path
As first revolution working oil path Bs the second revolution working oil path
FK feedback oil feeding line XD hydraulic control guide oil circuit
PJ1 first oil-feed oil circuit PJ2 the second oil-feed oil circuit
Embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is elaborated.Should be understood that, embodiment described herein only, for description and interpretation the present invention, is not limited to the present invention.
As shown in Figure 2, at first the present invention provides a kind of pilot operated directional control valve, this pilot operated directional control valve comprises valve body 1 and spool 2, spool 2 can axially movably be arranged in the valve pocket 3 of valve body 1, between the first end of the first end of this spool 2 and valve pocket 3, be formed with the first liquid controling cavity 6, and be formed with the second liquid controling cavity 7 between the second end of the second end of this spool 2 and valve pocket 3.In addition, this pilot operated directional control valve also comprises the first plunger 8 and the second plunger 9, this first plunger 8 and the second plunger 9 can axially movably be separately positioned in the first liquid controling cavity 6 and the second liquid controling cavity 7 and form cylinder and be sealed and matched, valve body 1 is provided with first and controls a mouthful A1, second controls a mouthful A2, the 3rd controls mouthful A3 and the 4th controls a mouthful A4, first controls a mouthful A1 is set to pass in the chamber between the first end of the first plunger 8 and valve pocket 3 of the first liquid controling cavity 6, second controls a mouthful A2 is set to pass in the chamber between the first end of the first plunger 8 and spool 1 of the first liquid controling cavity 6, the 3rd controls a mouthful A3 is set to pass in the chamber between the second end of the second plunger 9 and spool 1 of the second liquid controling cavity 7, the 4th controls a mouthful A4 is set to pass in the chamber between the second end of the second plunger 9 and valve pocket 3 of the second liquid controling cavity 7.The present invention's pilot operated directional control valve has herein been set up the first plunger 8 and the second plunger 9 in liquid controling cavity, and set up first and controlled mouthful A1 and the 4th a control mouthful A4, from these two controls mouthful, passing under the hydraulic pressure oil condition, can promote the valve port opening that described plunger in liquid controling cavity and spool 2 move effectively to regulate pilot operated directional control valve, thereby regulate by the hydraulic fluid flow rate of this pilot operated directional control valve, and can form throttling and then regulate hydraulic fluid pressure.This pilot operated directional control valve has extensive use, for example, below, will specifically set forth, at swing arm, completely struggle against while promoting the interlock with the revolution action, because completely struggling against, swing arm promotes required pressure higher than the required pressure of revolution, therefore this pilot operated directional control valve being set in the oil feeding line of rotary system can make the working connection hydraulic fluid flow rate that enters rotary system reduce, the pressure that enters the swing arm system increases, and promotes thereby drive swing arm, and the two produces coordination linkage.
About other structure of pilot operated directional control valve, referring to Fig. 2, wherein first control mouthful A1 and the 4th control mouthful A4 can the outside oil circuit of separate connection, also can be interconnected to connect outside single oil circuit, with the control mode corresponding to different.This pilot operated directional control valve structurally can carry out multiple improvement or variation, and for example the valve seat 10 at valve body 1 two ends can be integrally formed in the two ends of valve body 1, also can form the independent spring shield that is independent of valve body 1.The two ends of valve body 1 can be respectively equipped with plug section 4,5, form respectively described the first liquid controling cavity 6 and the second liquid controling cavity 7 between the two ends of spool 2 and corresponding plug section 4,5.And, this pilot operated directional control valve also can comprise the first spring 11 that is positioned at the first liquid controling cavity 6 and the second spring 12 that is positioned at the second liquid controling cavity 7, the first spring 11 and the second spring 12 all are set on the valve seat 10 of an end pressure-bearing in valve body 1, the other end is biased on the respective end of spool 2, with the first plunger 8 and the second plunger 9 actings in conjunction, on spool 2, to make it to move by control procedure.In the present embodiment, this pilot operated directional control valve is preferably three six-way transfer valves, valve body 1 is provided with oil inlet P 1, oil return inlet T 1, the first connecting port L1, the second connecting port L2, the first actuator port M1 and the second actuator port M2 be communicated in valve pocket 3, when spool 2 mediates, the first connecting port L1 is communicated with the second connecting port L2, and the first actuator port M1 and the second actuator port M2 all end conducting with oil inlet P 1 and oil return inlet T 1.It is can flow out from the second connecting port L2 for the interposition at pilot operated directional control valve also can make the hydraulic oil entered from the first connecting port L1 that the first connecting port L1 and the second connecting port L2 are set herein, forms the fluid path.
The interactive relationship of each structure member of pilot operated directional control valve when passing into hydraulic working oil is below described.Particularly, the first plunger 8 with valve seat 10 for forming the Spielpassung of cylinder sealing, the first plunger 8 can the valve pocket valve seat 10 in axially slippage, the second plunger 9 and valve seat 10 are similarly Spielpassung.When second controls mouth A2 oil-feed, can promote the first plunger 8 to left movement until contact with the first plug section 4, also can promote spool 2 and move right, spool 2 can promote the second plungers 9 to the right until contact with the second plug section 5; When the 3rd controls mouth A3 oil-feed, can promote the second plunger 9 to the right until contact with the second plug section 5, in the time of also can promoting spool 2 to left movement, spool 2 can promote the first plungers 8 and contact with the first plug section 4 to left movement.When first controls mouthful A1 and the 4th and controls mouthful A4 being interconnected as shown in Figure 3, first controls mouthful A1 or the 4th controls a mouthful A4 oil-feed meeting and promotes first plunger 8 and move right until contact with valve seat 10, also can promote the second plunger 9 to left movement until contact with valve seat 10 simultaneously.
On the basis of above-mentioned pilot operated directional control valve, the present invention is also corresponding provides a kind of interlock of this pilot operated directional control valve of application to control hydraulic system.As shown in Figure 3, the second operation control system 400 that hydraulic system comprises system oil-feed oil circuit P, system oil return oil circuit T, the first control valve 100 and the first operation control system 300 of controlling thereof and the second control valve 200 and control thereof is controlled in this interlock.Wherein, this first control valve 100 is above-mentioned according to pilot operated directional control valve of the present invention, and second in the first control valve 100 controlled a mouthful A2 and be connected with the first pilot control oil circuit XAs, and the 3rd controls a mouthful A3 is connected with the second pilot control oil circuit XBs.The second control valve 200 is pilot operated directional control valve, the both sides hydraulic control mouth of this pilot operated directional control valve is connected with respectively be used to the 3rd pilot control oil circuit XAb and the 4th pilot control oil circuit XBb that realizes that the guide is commutated, and the 3rd pilot control oil circuit XAb also is communicated with first in the first control valve 100 and controls mouthful A1 and the 4th a control mouthful A4.And system oil-feed oil circuit P is connected respectively to the oil return inlet T 1 of oil inlet P 2, the first control valves 100 of the oil inlet P 1 of the first control valve 100 and the second control valve 200 and the oil return inlet T 2 of the second control valve 200 all is connected to system oil return oil circuit T.This interlock control hydraulic system can effectively solve swing arm and stretch out (being that swing arm is fully loaded promotes) and rotating interlock harmony problem.Foregoing, its principle is to connect and arrange by pilot operated directional control valve (the first control valve 100) and corresponding guide's oil circuit as shown in Figure 3, make the first control valve 100 form throttling, hydraulic fluid pressure in system oil-feed oil circuit P raises, so that the more oil-feed fluid of high pressure to be provided to the second control valve 200, the driving swing arm stretches out, with the larger swing arm system works of dynamic load.So just reach the interlock of two different operation control systems of required hydraulic working oil pressure, avoid producing the only less system works of working pressure, and the larger system of working pressure has not produced the defect of corresponding actions.
In the present embodiment, the first control valve 100 and the second control valve 200 all are preferably three six-way transfer valves and comprise respectively oil inlet P 1, P2, oil return inlet T 1, T2, connecting port L1, L2, L3, L4 and actuator port M1, M2, N1, N2, wherein, the first connecting port L1 hydraulic connecting system oil-feed oil circuit P of the first control valve 100, the third connecting mouth L3 hydraulic connecting of the second connecting port L2 and the second control valve 200, the 4th connecting port L4 connected system oil return circuit T of the second control valve 200.Like this, when the first control valve 100 shown in Figure 3 and the second control valve 200 all mediated, each pilot control oil circuit was all without oil-feed, and each spool is without commutation.Pressure oil is from system oil-feed oil circuit P via the first control valve 100, the second control valve 200 and system oil return oil circuit T oil return unloading, and system is in unloading condition, the first operation control system 300 and the equal attonity of the second operation control system 400.
In interlock shown in Figure 3, control in hydraulic system, the second operation control system 400 comprises operating cylinder 13, the rod chamber Y of this operating cylinder is connected to the first actuator port N1 in the actuator port of the second control valve 200 by rod chamber working oil path Bb, the rodless cavity W of operating cylinder is connected to the second actuator port N2 in the actuator port of the second control valve 200 by rodless cavity working oil path Ab; Wherein, interlock is controlled hydraulic system and is also comprised the feedback selector valve 15 be arranged in rodless cavity working oil path Ab, in this feedback selector valve, be provided with the first hydraulic fluid port C1, the second hydraulic fluid port C2 and the 3rd hydraulic fluid port C3 and have the first commutation position and the second commutation position, the second actuator port N2 of first hydraulic fluid port C1 hydraulic connecting the second control valve 200, the rodless cavity W of the second hydraulic fluid port C2 hydraulic connecting operating cylinder 13, be connected with feedback oil feeding line FK between the oil inlet P 1 of the 3rd hydraulic fluid port C3 and the first control valve 100; At the first commutation position, the second hydraulic fluid port C2 is communicated with the first hydraulic fluid port C1 and is communicated with the 3rd hydraulic fluid port C3 cut-off, at the second commutation position, the second hydraulic fluid port C2 is communicated with by the first internal oil passages with the first hydraulic fluid port C1, and the second hydraulic fluid port C2 is communicated with by the second internal oil passages with the 3rd hydraulic fluid port C3 and the second internal oil passages is provided with first throttle valve 151.Aforesaid interlock is controlled in hydraulic system by arranging and according to pilot operated directional control valve of the present invention, can effectively be solved swing arm and stretch out (being that swing arm is fully loaded promotes) and rotating interlock harmony problem, herein by operating cylinder 13(boom cylinder) rodless cavity working oil path Ab and the first control valve 100(revolution control valve) oil inlet P 1 between the hydraulic element such as feedback oil feeding line FK and feedback selector valve 15 are set have also solved swing arm retraction (being that the swing arm zero load is transferred) and revolution and move the harmony problem linked.Its principle is, pressure during the swing arm retraction is lower, and rotating pressure is higher, therefore the hydraulic oil in the rodless cavity working oil path Ab of operating cylinder 13 is carried out to throttling by first throttle valve 151 grades, pressure oil after throttling is boosted turns back to the revolution control valve by feedback selector valve 15 and feedback oil feeding line FK, to drive the rotary motor running, make swing arm retraction and revolution co-ordination.
Wherein, when the 3rd pilot control oil circuit XAb passed into pressure oil and overcome so that the piston rod of operating cylinder 13 stretches out the load acting, feedback selector valve 15 was controlled to be and is in the next in Fig. 3, and rodless cavity working oil path Ab forms path in feedback selector valve 15.And only at the 4th pilot control oil circuit XBb, pass into pressure oil so that the piston rod of operating cylinder 13 when retraction, just control feedback selector valve 15 and be in upper and oil feeding line FK is fed back in conducting.The control of feedback selector valve 15 requires comparatively simple, can control by the electromagnet form, but for reliability and serviceability, consider in hydraulic system, in present embodiment, is preferably the hydraulic control mode.Namely feed back selector valve 15 and be pilot operated directional control valve, in the hydraulic control guide oil circuit XD of this feedback selector valve 15, be provided with pilot reversing valve 16 and shuttle valve 17, shuttle valve 17 has the first filler opening, the second filler opening and oil outlet, pilot reversing valve 16 has the first control port K1, first connects hydraulic fluid port B1, second connects hydraulic fluid port B2 is connected hydraulic fluid port B3 with the 3rd, control port K1 hydraulic connecting the 4th pilot control oil circuit XBb, first connects the second control port K2 of hydraulic fluid port B1 hydraulic connecting feedback selector valve 15, second connects hydraulic fluid port B2 hydraulic connecting system oil return oil circuit T, the 3rd connects the oil outlet of hydraulic fluid port B3 hydraulic connecting shuttle valve 17, and the first filler opening of shuttle valve 17 connects the first pilot control oil circuit XAs, the second filler opening connects the second pilot control oil circuit XBs.In the hydraulic control guide oil circuit XD of this feedback selector valve 15, the first control port K1 hydraulic connecting the 4th pilot control oil circuit XBb due to pilot reversing valve 16, only at the 4th pilot control oil circuit XBb, pass into hydraulic oil and make piston rod when retraction of operating cylinder 13, pilot reversing valve 16 just switches to right position, the first pilot control oil circuit XAs and the higher hydraulic oil of pressure in the second pilot control oil circuit XBs that shuttle valve 17 is introduced are guided to the second control port K2 that feeds back selector valve 15, make the valve position switching of feedback selector valve 15, conducting rodless cavity working oil path Ab and feedback oil feeding line FK.And while in the 4th pilot control oil circuit XBb, not passing into hydraulic oil, pilot reversing valve 16 is all the time for left position, the second control port K2 hydraulic communication system oil return oil circuit T or oil sump tank of feedback selector valve 15, feedback selector valve 15 remains at lower rest position.
In order to strengthen the throttling action to the hydraulic oil in rodless cavity working oil path Ab, on the second internal oil passages of feedback selector valve 15, arrange on the basis of first throttle valve 151, in the second control valve 200, also be provided with the second throttle valve 201, with the restriction effect of returning home.With reference to Fig. 3, the control bit that the 4th pilot control oil circuit XBb is corresponding (the right position in Fig. 3) is arranged so that the first actuator port N1 is communicated with oil inlet P 2, the second actuator port N2 and connects oil circuit connection oil return inlet T 2 and should in inside connection oil circuit, be provided with the second throttle valve 201 by inside.
In addition, for strengthening the reliability of operating cylinder 13, in its working oil path, also be provided with one-way hydraulic lock 14, this one-way hydraulic lock 14 be arranged on the operating cylinder 13 in rodless cavity working oil path Ab rodless cavity W and the feedback selector valve 15 the second hydraulic fluid port C2 between the oil circuit part on.When the piston rod of operating cylinder 13 stretched out, the high pressure liquid force feed in rodless cavity working oil path Ab was opened the one-way valve in one-way hydraulic lock 14 and is entered rodless cavity W.And rod chamber working oil path Bb connected system oil return circuit T be connected to the control mouth of one-way hydraulic lock 14, because oil pressure pressure is low, be difficult to make one-way hydraulic lock 14 reverse-conductings, be that hydraulic oil in rodless cavity W is difficult to reflux to the second control valve 200 by rodless cavity working oil path Ab, reliability and Security during with the piston rod work of safeguard work oil cylinder 13.When the piston rod of operating cylinder 13 is retracted, in rod chamber working oil path Bb, pass into high pressure oil, this high pressure oil can make one-way hydraulic lock 14 reverse-conductings as pilot control oil, and the hydraulic oil in rodless cavity W can reflux by rodless cavity working oil path Ab.
In addition, a plurality of one-way valves that also have been provided with safety effect in each oil circuit in hydraulic system are controlled in this interlock.In feedback oil feeding line FK shown in Figure 3, also be provided with feedback one-way valve 18 to guarantee the one-way hydraulic feedback, this feedback one-way valve 18 is arranged so that hydraulic oil can flow to from the 3rd hydraulic fluid port C3 of feedback selector valve 15 the first oil inlet P 1 of the first control valve 100 and oppositely cut-off.Interlock is controlled hydraulic system and is also comprised the first in line check valve 19 and the second in line check valve 20, system oil-feed oil circuit P hydraulic connecting is to the first connecting port L1 of the first control valve 100, and by the first oil-feed oil circuit PJ1 and the second oil-feed oil circuit PJ2 respectively to the oil inlet P 1 of the first control valve 100 and oil inlet P 2 fuel feeding of the second control valve 200, the end hydraulic connecting second oil-feed oil circuit PJ2 of the first oil-feed oil circuit PJ1, the other end are connected on the oil inlet P at the first control valve 100 1 and the oil circuit part between feedback one-way valve 18 of feedback oil feeding line FK.The first in line check valve 19 is arranged in the second oil-feed oil circuit PJ2, so that hydraulic oil can flow to the oil inlet P 2 of the second control valve 200 and oppositely cut-off from system oil-feed oil circuit P, thus unidirectional fuel feeding only.The second in line check valve 20 is arranged on the first oil-feed oil circuit PJ1, so that hydraulic oil can flow to from system oil-feed oil circuit P the oil inlet P 1 of the first control valve 100 by the first oil-feed oil circuit PJ1, and can not make the hydraulic oil in the oil inlet P 1 of the first control valve 100 by the first oil-feed oil circuit PJ1, flow back into the second oil-feed oil circuit PJ2 and indirectly flow back into system oil-feed oil circuit P, the hydraulic oil in the oil inlet P 1 of the first control valve 100 can directly flow back into system oil-feed oil circuit P.Simultaneously, the feedback hydraulic oil in feedback oil feeding line FK can only feed back to the oil inlet P 1 of the first control valve 100 and can not branch to the oil inlet P 2 of the second control valve 200, guarantees that the hydraulic oil at oil inlet P 1 place of the first control valve 100 does not produce pressure release.
Above-mentioned interlock is controlled hydraulic system and be may be used on multiple interlock control occasion, for example, in the time of on being applied to hydraulic shovel, can form the hydraulic control system of excavator of the present invention.Now, 300 of the first above-mentioned operation control systems are the revolution operation control system, the second operation control system 400 is the swing arm operation control system, the 3rd pilot control oil circuit XAb carries out stretch for the boom cylinder of controlling the swing arm operation control system, and the 4th pilot control oil circuit XBb carries out the action of contracting arm for the boom cylinder of controlling the swing arm operation control system.
Referring to Fig. 2 and Fig. 3, elaborate concrete operating mode and control procedure thereof according to the hydraulic control system of excavator of the present invention.
1, revolution single action: the first pilot control oil circuit XAs(or the second pilot control oil circuit XBs) oil-feed, the 3rd pilot control oil circuit XAb, the 4th not oil-feed of pilot control oil circuit XBb.Revolution control valve (i.e. the first control valve 100) can be at first pilot control oil circuit XAs(the second pilot control oil circuit XBs) the lower commutation of effect is to right position shown in Figure 3 (or left position), system pressure oil enters the first revolution working oil path As(or the second revolution working oil path Bs via the first oil-feed oil circuit PJ1 that is provided with the second in line check valve 20) rotation of drive rotary motor.The oil return of rotary motor is via the second revolution working oil path Bs(or the first revolution working oil path As) by the revolution control valve, be communicated with system oil return oil circuit T, thus revolution starts to rotate.
2, swing arm single action: if the 3rd pilot control oil circuit XAb oil-feed, the first pilot control oil circuit XAs, the second not oil-feed of pilot control oil circuit XBs, feedback selector valve 15 is in shown in Figure 3 the next.Swing arm control valve (i.e. the second control valve 200) can commutate to left position under the 3rd pilot control oil circuit XAb effect, system pressure oil is via the first in line check valve 19, swing arm control valve, feedback selector valve 15, open the one-way valve of one-way hydraulic lock 14, via rodless cavity working oil path Ab, enter the rodless cavity W of boom cylinder (being operating cylinder 13).The hydraulic oil of the rod chamber Y of boom cylinder is connected with system oil return oil circuit T via rod chamber working oil path Bb, swing arm control valve, thereby boom cylinder stretches out.If the 4th pilot control oil circuit XBb oil-feed, the first pilot control oil circuit XAs, the second not oil-feed of pilot control oil circuit XBs, feedback selector valve 15 is in shown in Figure 3 the next.The swing arm control valve can commutate to right position under the 4th pilot control oil circuit XBb effect, system pressure oil enters the rod chamber Y of boom cylinder via the first in line check valve 19, swing arm control valve, rod chamber working oil path Bb.The hydraulic oil of the rodless cavity Y of boom cylinder can be opened and make its reverse opening by the pressure oil in rod chamber working oil path Bb via rodless cavity working oil path Ab, one-way hydraulic lock 14(), the swing arm control valve is connected with system oil return oil circuit T.Thereby boom cylinder is retracted.
3, boom cylinder stretches out and the revolution interlock: when the 3rd pilot control oil circuit XAb oil-feed, the 3rd pilot control oil circuit XAb makes the commutation of swing arm control valve.Meanwhile, the spring force that the first pilot control oil circuit XAs oil-feed makes the spool 2 in the revolution control valve overcome the second spring 12 moves right, and the 3rd pilot control oil circuit XAb makes the second plunger 9 to left movement.When spool 2 contacts with the second plunger 9, act on pressure that spool 2 axial force to the right is the first pilot control oil circuit XAs and the product of spool 2 diameter areas, act on spring force, 9 pairs of spools 2 of the second plunger end thrust (being the pressure of the 3rd pilot control oil circuit XAb and the product of the second plunger 9 diameter areas) left that spool 2 axial force left is the second spring 12, and spool 2 axial force to the right is less than spool 2 axial force left.Therefore the second plunger 9 can hinder that spools 2 move right and the second plunger 9 can contact with valve seat 10.So when the first pilot control oil circuit XAs and the 3rd pilot control oil circuit XAb oil-feed simultaneously, the displacement when displacement of the spool 2 in the revolution control valve is less than the independent oil-feed of the first pilot control oil circuit XAs, the oil inlet passage that turns round the oil inlet P 1 in control valve is less, produce throttling, make the pressure oil-source in system oil-feed oil circuit P boost, thereby promote the higher boom cylinder of load, stretch out, the higher boom cylinder of the lower revolution action of load and load stretches out simultaneously and carries out.In like manner, the two can also link when the 3rd pilot control oil circuit XAb and the second pilot control oil circuit XBs oil-feed.
4, boom cylinder is retracted and the revolution interlock: in conjunction with Fig. 3, when the first pilot control oil circuit XAs and the 4th pilot control oil circuit XBb oil-feed simultaneously, the first pilot control oil circuit XAs makes revolution handle commutation, the 4th pilot control oil circuit XBb makes the commutation of swing arm control valve and makes pilot reversing valve 16 commutations, and the first pilot control oil circuit XAs makes to feed back selector valve 15 commutations through shuttle valve 17, pilot reversing valve 16.Because boom cylinder retraction load is lower, boom cylinder starts retraction, hydraulic oil in the rodless cavity W of boom cylinder enters the upper of feedback selector valve 15 through rodless cavity working oil path Ab, first segment discharge orifice 151, the swing arm control valve of a part in feedback selector valve 15 is back to system oil return oil circuit T, and another part feeds back to the oil inlet P 1 of revolution control valve through feedback selector valve 15, feedback one-way valve 18.On the one hand, under the weight effect, in the rodless cavity W of boom cylinder, elevated pressures is arranged, if this pressure is higher than turning round load, the feedback pressure oil in the rodless cavity W of boom cylinder can drive the rotary motor rotation; On the other hand, if the pressure in the rodless cavity W of boom cylinder is lower than the revolution load, the hydraulic oil in the rodless cavity W of boom cylinder produces throttling via the throttle valve in feedback selector valve 15 and swing arm control valve, make the pressure oil in feedback oil feeding line FK boost, rotate thereby drive rotary motor.So when the first pilot control oil circuit XAs, the 4th pilot control oil circuit XBb oil-feed simultaneously, can realize that the lower boom cylinder of load is retracted and move simultaneously with the higher revolution of load, as the same when the second pilot control oil circuit XBs, the 4th pilot control oil circuit XBb oil-feed simultaneously.
As fully visible, the present invention has following advantage:
1, simple in structure, convenient for installation and maintenance;
2, by hydraulic pressure signal, each hydraulic control valve, realize hydraulic control, automation is high, and reliability is strong;
3, realized that boom cylinder stretches out, retraction and rotating whole interlock, the two action is coordinated more, improved the navigability of hydraulic shovel.
Below describe by reference to the accompanying drawings the preferred embodiment of the present invention in detail; but; the present invention is not limited to the detail in above-mentioned mode of execution; in technical conceive scope of the present invention; can carry out multiple simple variant to technological scheme of the present invention, these simple variant all belong to protection scope of the present invention.
It should be noted that in addition, each concrete technical characteristics described in above-mentioned embodiment, in reconcilable situation, can combine by any suitable mode, for fear of unnecessary repetition, the present invention is to the explanation no longer separately of various possible compound modes.
In addition, also can carry out combination in any between various mode of execution of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.
Claims (14)
1. pilot operated directional control valve, comprise valve body (1) and spool (2), described spool (2) can axially movably be arranged in the valve pocket (3) of described valve body (1), between the first end of the first end of this spool (2) and described valve pocket (3), be formed with the first liquid controling cavity (6), and between the second end of second end of this spool (2) and described valve pocket (3), be formed with the second liquid controling cavity (7), it is characterized in that, described pilot operated directional control valve also comprises the first plunger (8) and the second plunger (9), this first plunger (8) and the second plunger (9) can axially movably be separately positioned in described the first liquid controling cavity (6) and the second liquid controling cavity (7) and form cylinder and be sealed and matched, described valve body (1) is provided with first and controls mouthful (A1), second controls mouthful (A2), the 3rd controls mouthful (A3) and the 4th controls mouthful (A4), described first controls the chamber between the first end that mouthful (A1) be set to pass into described the first plunger of being positioned at of described the first liquid controling cavity (6) (8) and described valve pocket (3), described second controls the chamber between the first end that mouthful (A2) be set to pass into described the first plunger of being positioned at of described the first liquid controling cavity (6) (8) and described spool (1), the described the 3rd controls the chamber between the second end that mouthful (A3) be set to pass into described the second plunger of being positioned at of described the second liquid controling cavity (7) (9) and described spool (1), the described the 4th controls the chamber between the second end that mouthful (A4) be set to pass into described the second plunger of being positioned at of described the second liquid controling cavity (7) (9) and described valve pocket (3).
2. pilot operated directional control valve according to claim 1, is characterized in that, described the first control mouthful (A1) and the 4th is controlled mouthful (A4) and is interconnected.
3. pilot operated directional control valve according to claim 1, it is characterized in that, the two ends of described valve body (1) are respectively equipped with plug section (4,5), between the two ends of described spool (2) and corresponding described plug section (4,5), form respectively described the first liquid controling cavity (6) and the second liquid controling cavity (7).
4. pilot operated directional control valve according to claim 1, it is characterized in that, this pilot operated directional control valve also comprises the first spring (11) that is positioned at described the first liquid controling cavity (6) and the second spring (12) that is positioned at described the second liquid controling cavity (7), it is upper that described the first spring (11) and the second spring (12) all are set to the valve seat (10) of an end pressure-bearing in described valve body (1), and the other end is biased on the respective end of described spool (2).
5. according to the described pilot operated directional control valve of any one in claim 1-4, it is characterized in that, this pilot operated directional control valve is three six-way transfer valves, described valve body (1) is provided with the filler opening (P1) be communicated in described valve pocket (3), return opening (T1), the first connecting port (L1), the second connecting port (L2), the first actuator port (M1) and the second actuator port (M2), described spool (2) is while mediating, described the first connecting port (L1) is communicated with described the second connecting port (L2), and described the first actuator port (M1) and the second actuator port (M2) all end conducting with described filler opening (P1) and return opening (T1).
6. hydraulic system is controlled in an interlock, comprise system oil-feed oil circuit (P), system oil return oil circuit (T), the first control valve (100) and the first operation control system (300) of controlling thereof and the second control valve (200) and the second operation control system (400) of controlling thereof, it is characterized in that:
Described the first control valve (100) is according to the described pilot operated directional control valve of any one in the claims 1-5, in described the first control valve (100) described second controlled mouthful (A2) and is connected with the first pilot control oil circuit (XAs), and the described the 3rd controls mouthful (A3) is connected with the second pilot control oil circuit (XBs);
Described the second control valve (200) is pilot operated directional control valve, the both sides hydraulic control mouth of this pilot operated directional control valve is connected with respectively be used to the 3rd pilot control oil circuit (XAb) and the 4th pilot control oil circuit (XBb) of realizing that the guide is commutated, and described the 3rd pilot control oil circuit (XAb) also is communicated with described first in described the first control valve (100) and controls mouthful (A1) and the 4th control mouthful (A4);
And described system oil-feed oil circuit (P) is connected respectively to the filler opening (P1) of described the first control valve (100) and the filler opening (P2) of the second control valve (200), the return opening (T1) of described the first control valve (100) and the return opening (T2) of the second control valve (200) all are connected to described system oil return oil circuit (T).
7. hydraulic system is controlled in interlock according to claim 6, it is characterized in that, described the first control valve (100) and the second control valve (200) are three six-way transfer valves and comprise respectively filler opening (P1, P2), return opening (T1, T2), connecting port (L1, L2, L3, L4) and actuator port (M1, M2, N1, N2), wherein, the first connecting port (L1) hydraulic connecting described system oil-feed oil circuit (P) of described the first control valve (100), third connecting mouth (L3) hydraulic connecting of the second connecting port (L2) and the second control valve (200), the 4th connecting port (L4) of described the second control valve (200) is communicated with described system oil return oil circuit (T).
8. hydraulic system is controlled in interlock according to claim 6, it is characterized in that, described the second operation control system (400) comprises operating cylinder (13), the rod chamber of this operating cylinder (Y) is connected to the first actuator port (N1) in the described actuator port of described the second control valve (200) by rod chamber working oil path (Bb), the rodless cavity of described operating cylinder (W) is connected to the second actuator port (N2) in the described actuator port of described the second control valve (200) by rodless cavity working oil path (Ab);
Wherein, described interlock is controlled hydraulic system and is also comprised the feedback selector valve (15) be arranged in described rodless cavity working oil path (Ab), in this feedback selector valve, be provided with the first hydraulic fluid port (C1), the second hydraulic fluid port (C2) and the 3rd hydraulic fluid port (C3) and have the first commutation position and the second commutation position, second actuator port (N2) of described the second control valve of described the first hydraulic fluid port (C1) hydraulic connecting (200), the rodless cavity (W) of the described operating cylinder of described the second hydraulic fluid port (C2) hydraulic connecting (13), between the described filler opening (P1) of described the 3rd hydraulic fluid port (C3) and described the first control valve (100), be connected with feedback oil feeding line (FK), at described the first commutation position, described the second hydraulic fluid port (C2) is communicated with the first hydraulic fluid port (C1) and is communicated with described the 3rd hydraulic fluid port (C3) cut-off, at described the second commutation position, described the second hydraulic fluid port (C2) is communicated with by the first internal oil passages with the first hydraulic fluid port (C1), and described the second hydraulic fluid port (C2) is communicated with by the second internal oil passages with the 3rd hydraulic fluid port (C3) and described the second internal oil passages is provided with first throttle valve (151).
9. hydraulic system is controlled in interlock according to claim 8, it is characterized in that, in described the second control valve (200), control bit corresponding to described the 4th pilot control oil circuit (XBb) is arranged so that described the first actuator port (N1) is communicated with described filler opening (P2), described the second actuator port (N2) connects oil circuit by inside and is communicated with described return opening (T2), and described inner the connection in oil circuit is provided with the second throttle valve (201).
10. hydraulic system is controlled in interlock according to claim 8, it is characterized in that, described feedback selector valve (15) is pilot operated directional control valve, in the hydraulic control guide oil circuit (XD) of this feedback selector valve (15), be provided with pilot reversing valve (16) and shuttle valve (17), described shuttle valve (17) has the first filler opening, the second filler opening and oil outlet, described pilot reversing valve (16) has the first control port (K1), first connects hydraulic fluid port (B1), second connects hydraulic fluid port (B2) is connected hydraulic fluid port (B3) with the 3rd, described the 4th pilot control oil circuit (XBb) of described control port (K1) hydraulic connecting, described first connects second control port (K2) of hydraulic fluid port (B1) the described feedback selector valve of hydraulic connecting (15), described second connects hydraulic fluid port (B2) the described system oil return oil circuit of hydraulic connecting (T), the described the 3rd connects the oil outlet of the described shuttle valve of hydraulic fluid port (B3) hydraulic connecting (17), and the first filler opening of described shuttle valve (17) connects described the first pilot control oil circuit (XAs), the second filler opening connects described the second pilot control oil circuit (XBs).
11. hydraulic system is controlled in interlock according to claim 8, it is characterized in that, described interlock is controlled hydraulic system and is also comprised one-way hydraulic lock (14), and this one-way hydraulic lock is arranged on the oil circuit part between second hydraulic fluid port (C2) of the rodless cavity (W) of the described operating cylinder (13) in described rodless cavity working oil path (Ab) and described feedback selector valve (15).
12. hydraulic system is controlled in interlock according to claim 8, it is characterized in that, in described feedback oil feeding line (FK), be provided with feedback one-way valve (18), this feedback one-way valve is arranged so that hydraulic oil can flow to from the 3rd hydraulic fluid port (C3) of described feedback selector valve (15) first filler opening (P1) of described the first control valve (100) and oppositely cut-off.
13. hydraulic system is controlled in interlock according to claim 12, it is characterized in that, described system oil-feed oil circuit (P) by the first oil-feed oil circuit (PJ1) and the second oil-feed oil circuit (PJ2) respectively to the filler opening (P1) of described the first control valve (100) and filler opening (P2) fuel feeding of described the second control valve (200), described the second oil-feed oil circuit (PJ2) of one end hydraulic connecting of described the first oil-feed oil circuit (PJ1), the other end hydraulic connecting is on the filler opening (P1) and the oil circuit part between described feedback one-way valve (18) of described the first control valve of being positioned at of described feedback oil feeding line (FK) (100),
Wherein, described interlock is controlled hydraulic system and is also comprised the first in line check valve (19) and the second in line check valve (20), described the first in line check valve (19) is arranged in described the second oil-feed oil circuit (PJ2), so that hydraulic oil can flow to the filler opening (P2) of described the second control valve (200) and oppositely cut-off from described system oil-feed oil circuit (P);
It is upper that described the second in line check valve (20) is arranged on described the first oil-feed oil circuit (PJ1), so that hydraulic oil can flow to the filler opening (P1) of described the first control valve (100) and oppositely cut-off by described the first oil-feed oil circuit (PJ1) from described system oil-feed oil circuit (P).
14. the hydraulic control system of an excavator, it is characterized in that, the hydraulic control system of this excavator comprises that hydraulic system is controlled in described interlock according to any one in the claims 6 to 13, wherein said the first operation control system (300) is the revolution operation control system, described the second operation control system (400) is the swing arm operation control system, described the 3rd pilot control oil circuit (XAb) is carried out stretch be used to controlling described swing arm operation control system, described the 4th pilot control oil circuit (XBb) is carried out the action of contracting arm be used to controlling described swing arm operation control system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310351081.5A CN103410803B (en) | 2013-08-13 | 2013-08-13 | The hydraulic control system of pilot operated directional control valve, coordinated signals hydraulic system and excavator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310351081.5A CN103410803B (en) | 2013-08-13 | 2013-08-13 | The hydraulic control system of pilot operated directional control valve, coordinated signals hydraulic system and excavator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103410803A true CN103410803A (en) | 2013-11-27 |
| CN103410803B CN103410803B (en) | 2015-11-25 |
Family
ID=49603835
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310351081.5A Active CN103410803B (en) | 2013-08-13 | 2013-08-13 | The hydraulic control system of pilot operated directional control valve, coordinated signals hydraulic system and excavator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103410803B (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105545842A (en) * | 2016-02-05 | 2016-05-04 | 魏英群 | TRT static blade actuator synchronization control system and control method |
| CN105621294A (en) * | 2016-01-29 | 2016-06-01 | 武汉船用机械有限责任公司 | Hydraulically-controlled operation dual-variable-amplitude synchronous adjustment control valve group |
| CN108019392A (en) * | 2018-01-27 | 2018-05-11 | 宁波市博尔法液压有限公司 | A kind of hydraulic lock |
| CN108252977A (en) * | 2018-02-05 | 2018-07-06 | 陈艳艳 | A kind of oil path distribution valve for large-flow hydraulic system |
| CN110056587A (en) * | 2019-04-08 | 2019-07-26 | 浙江大学 | A kind of dual fail-safe fast braking hydraulic circuit based on marine tidal-current energy generator group |
| CN110158697A (en) * | 2019-06-14 | 2019-08-23 | 江苏徐工工程机械研究院有限公司 | Signal cut valve and hydraulic control system |
| CN110821908A (en) * | 2019-11-07 | 2020-02-21 | 杭州发达齿轮箱集团有限公司 | Marine gearbox reversing valve capable of being connected and arranged quickly and control method thereof |
| CN113431127A (en) * | 2021-07-27 | 2021-09-24 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN114207295A (en) * | 2021-11-15 | 2022-03-18 | 无锡市东舟船舶设备股份有限公司 | Hydraulic system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB783172A (en) * | 1953-05-28 | 1957-09-18 | Pultra Ltd | An improved hydraulic control |
| GB820704A (en) * | 1957-03-25 | 1959-09-23 | Curtiss Wright Corp | Improvements in or relating to hydraulic motors |
| GB860182A (en) * | 1956-04-11 | 1961-02-01 | Mipsa Sa | Improvements in or relating to hydraulic control installations |
| GB1202358A (en) * | 1966-10-14 | 1970-08-19 | Dowty Mining Equipment Ltd | Mine roof support systems |
| CN2166271Y (en) * | 1993-02-26 | 1994-05-25 | 阳泉矿务局煤炭科学研究所 | Multi-way liquid control link change valve |
| CN201125895Y (en) * | 2007-11-20 | 2008-10-01 | 梁志强 | Liquid control reversing valve |
| CN101793042A (en) * | 2009-12-31 | 2010-08-04 | 福田雷沃国际重工股份有限公司 | Hydraulic loop device used for coordinating machine body rotation and movable arm swinging of digging machine |
-
2013
- 2013-08-13 CN CN201310351081.5A patent/CN103410803B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB783172A (en) * | 1953-05-28 | 1957-09-18 | Pultra Ltd | An improved hydraulic control |
| GB860182A (en) * | 1956-04-11 | 1961-02-01 | Mipsa Sa | Improvements in or relating to hydraulic control installations |
| GB820704A (en) * | 1957-03-25 | 1959-09-23 | Curtiss Wright Corp | Improvements in or relating to hydraulic motors |
| GB1202358A (en) * | 1966-10-14 | 1970-08-19 | Dowty Mining Equipment Ltd | Mine roof support systems |
| CN2166271Y (en) * | 1993-02-26 | 1994-05-25 | 阳泉矿务局煤炭科学研究所 | Multi-way liquid control link change valve |
| CN201125895Y (en) * | 2007-11-20 | 2008-10-01 | 梁志强 | Liquid control reversing valve |
| CN101793042A (en) * | 2009-12-31 | 2010-08-04 | 福田雷沃国际重工股份有限公司 | Hydraulic loop device used for coordinating machine body rotation and movable arm swinging of digging machine |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105621294A (en) * | 2016-01-29 | 2016-06-01 | 武汉船用机械有限责任公司 | Hydraulically-controlled operation dual-variable-amplitude synchronous adjustment control valve group |
| CN105545842A (en) * | 2016-02-05 | 2016-05-04 | 魏英群 | TRT static blade actuator synchronization control system and control method |
| CN108019392B (en) * | 2018-01-27 | 2024-04-23 | 宁波市博尔法液压有限公司 | Hydraulic lock |
| CN108019392A (en) * | 2018-01-27 | 2018-05-11 | 宁波市博尔法液压有限公司 | A kind of hydraulic lock |
| CN108252977A (en) * | 2018-02-05 | 2018-07-06 | 陈艳艳 | A kind of oil path distribution valve for large-flow hydraulic system |
| CN110056587A (en) * | 2019-04-08 | 2019-07-26 | 浙江大学 | A kind of dual fail-safe fast braking hydraulic circuit based on marine tidal-current energy generator group |
| CN110158697A (en) * | 2019-06-14 | 2019-08-23 | 江苏徐工工程机械研究院有限公司 | Signal cut valve and hydraulic control system |
| CN110158697B (en) * | 2019-06-14 | 2024-04-30 | 江苏徐工工程机械研究院有限公司 | Signal cut-off valve and hydraulic control system |
| CN110821908A (en) * | 2019-11-07 | 2020-02-21 | 杭州发达齿轮箱集团有限公司 | Marine gearbox reversing valve capable of being connected and arranged quickly and control method thereof |
| CN110821908B (en) * | 2019-11-07 | 2024-05-03 | 杭州发达齿轮箱集团有限公司 | Marine gearbox reversing valve capable of being connected and discharged quickly and control method thereof |
| CN113431127B (en) * | 2021-07-27 | 2024-03-22 | 广西中源机械有限公司 | Main control valve, constant-variable hydraulic system and loader |
| CN113431127A (en) * | 2021-07-27 | 2021-09-24 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| WO2023082234A1 (en) * | 2021-11-15 | 2023-05-19 | 无锡市东舟船舶设备股份有限公司 | Hydraulic system |
| CN114207295B (en) * | 2021-11-15 | 2024-04-05 | 无锡市东舟船舶设备股份有限公司 | Hydraulic system |
| CN114207295A (en) * | 2021-11-15 | 2022-03-18 | 无锡市东舟船舶设备股份有限公司 | Hydraulic system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103410803B (en) | 2015-11-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103410803B (en) | The hydraulic control system of pilot operated directional control valve, coordinated signals hydraulic system and excavator | |
| US20130098464A1 (en) | Closed-Loop Hydraulic System Having Regeneration Configuration | |
| CN203532390U (en) | Hydraulic cylinder quick motion loop and engineering machine | |
| CN108316389B (en) | Multi-way valve for wheel excavator | |
| CN104747535A (en) | Hydraulic buffering system and engineering machine | |
| CN104863914A (en) | Electrohydraulic joint control flow collecting valve | |
| CN104235102A (en) | Upper hydraulic system and engineering machinery | |
| CN104074825A (en) | Two-way selection type convergence load sensing multi-way valve | |
| US8966892B2 (en) | Meterless hydraulic system having restricted primary makeup | |
| JP2022507986A (en) | Regenerative control hydraulic system | |
| CN113494111B (en) | Main control valve, fixed variable hydraulic system and loader | |
| CN113482090B (en) | Main control valve, constant-variable hydraulic system and loader | |
| CN201096115Y (en) | Hydraulic combined valve | |
| CN203570713U (en) | Load sensing hydraulic control system and engineering machine | |
| CN103015483B (en) | Time delay brake system of hydraulic slewing device and engineering machine | |
| CN202381429U (en) | Forward jumping prevention control valve of crane telescopic oil cylinder and crane telescopic system | |
| US20180106277A1 (en) | Valve device and fluid pressure control device | |
| CN105422530B (en) | Guide's integrated multipath valve group and crane | |
| CN103470556A (en) | Multi-way valve converging hydraulic system and land leveler | |
| CN106762903B (en) | Multiple directional control valve | |
| CN205895730U (en) | Oil drilling equipment , elevator and hydraulic system thereof | |
| CN114542540A (en) | Flow regeneration hydraulic system and engineering machinery | |
| CN114517798A (en) | Hydraulic drive system and working machine | |
| CN104481944A (en) | Depressurizing system and engineering machinery | |
| CN106812752A (en) | Multiple directional control valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |